US5349818A - Low deadband marine hydraulic steering system - Google Patents
Low deadband marine hydraulic steering system Download PDFInfo
- Publication number
- US5349818A US5349818A US08/104,642 US10464293A US5349818A US 5349818 A US5349818 A US 5349818A US 10464293 A US10464293 A US 10464293A US 5349818 A US5349818 A US 5349818A
- Authority
- US
- United States
- Prior art keywords
- port
- spool
- passageway
- valve
- bore
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Ceased
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
- B63H25/06—Steering by rudders
- B63H25/08—Steering gear
- B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
- B63H25/18—Transmitting of movement of initiating means to steering engine
- B63H25/22—Transmitting of movement of initiating means to steering engine by fluid means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/2496—Self-proportioning or correlating systems
- Y10T137/2544—Supply and exhaust type
- Y10T137/2554—Reversing or 4-way valve systems
Definitions
- This invention relates to marine hydraulic steering systems and hydraulic lock valves used in conjunction therewith.
- Hydraulic steering systems are preferred on small pleasure and fishing boats instead of the more usual cable steering systems.
- a problem is encountered however in conventional hydraulic steering systems when they are used on high power boats in particular.
- Such systems normally include a reversible rotary pump which is mechanically coupled to the steering wheel. Hydraulic lines extend from this manual pump to a hydraulic cylinder attached to the outboard motor or inboard/outboard motor.
- Hydraulic lines extend from this manual pump to a hydraulic cylinder attached to the outboard motor or inboard/outboard motor.
- a high force is exerted on the cylinder, and consequently on the steering wheel, by the rudder or engine torque.
- the boater must maintain a hold on the wheel to keep the boat on course.
- a dangerous hard-over motion of the engine can result. This can even throw a person out of the boat or cause the boat to circle back and run over a person who has fallen out of the boat.
- lock valves are often included in the same housing as the pump connected to the steering wheel, but they could be separate and located in different places such as the back of the boat near the motor.
- these valves include two ports which are connected to the pump and two ports which are connected to the cylinder for two line hydraulic systems. In such systems the two ports on the pump alternate as intake and discharge ports depending upon the direction the steering wheel is turned.
- the lock valve usually includes an internal spool valve and two check valves or popper valves. When the wheel is rotated, pressurized fluid from the pump enters one of the ports on the lock valve.
- the pressurized fluid forces open one of the check valves or poppet valves, thus allowing the fluid to discharge from one of the ports towards the hydraulic cylinder.
- Hydraulic fluid returning from the other side of the cylinder must reach the intake side of the, pump. Normally this flow is blocked by the other check valve.
- the spool valve is shifted by the pressurized fluid from the pump and pushes against the second check valve, opening a return passageway for fluid.
- one aspect of the invention provides a hydraulic control apparatus which includes a reversible, manual pump having two ports.
- a lock valve having a body with a bore and a valve spool reciprocatingly received within the bore.
- a first port of the valve is connected to one of the pump ports.
- a second port of the lock valve is connected to another pump port.
- the lock valve also has third and fourth ports. The lock valve permits a flow of fluid from the first port to the third port when the first port is pressurized. It permits a fluid flow from the third port to the first port only when the second port is pressurized.
- the lock valve permits a fluid flow from the second port to the fourth port when the second port is pressurized and permits a flow of fluid from the fourth port to the second port only when the first port is pressurized.
- There is a second passageway having a first portion extending from the fourth port to the bore and a second portion extending from the bore to the second port.
- the spool normally blocks fluid flow between the two portions.
- the spool has an opening which interconnects the two portions when the spool is shifted in one direction.
- There is a third passageway extending from the first port to the bore adjacent a first end of the spool to shift the spool in the one direction when the first port is pressurized.
- a lock valve which includes a body and a spool valve in the body with a bore and a valve spool reciprocatingly received therein.
- the spool has a passageway.
- Second means permits a fluid flow from the first port to the third port when the first port is pressurized.
- Third means permits a fluid flow from the third port to the first port when the second port is pressurized.
- Fifth means permits a flow of fluid from the fourth port to the second port when the first port is pressurized.
- a first passageway extends from the fourth port to the bore.
- a second passageway extends from the bore to the second port. Flow between the fourth port and the first port is normally blocked by the valve spool.
- the fifth means includes a third passageway from the first port to the bore adjacent one end of the spool, whereby the spool is shifted in a first direction when the first port is pressurized.
- a fourth passageway in the spool valve interconnects the first passageway and the second passageway through the bore when the spool is so shifted in the first direction.
- the invention overcomes problems associated with the prior art by allowing a return flow of fluid from the hydraulic cylinder to the steering pump without requiring sufficient pressure on the valve spool to unseat a check valve against the pressure of fluid acting on the return line from the cylinder. Instead, the return line is opened by the simple shifting of the valve spool itself by hydraulic pressure from the discharge port of the pump. The movement of the spool opens a passageway through the spool valve itself for the return flow of fluid to the pump.
- the degree of pressurization is significantly reduced.
- the deadband has been reduced to only 4°-9° in embodiments of the invention. In other words, the deadband has been reduced approximately 90% compared with prior art hydraulic steering systems using a conventional lock valve.
- the invention permits the lock valve to be manufactured with relatively minor modifications to conventional lock valve designs, thus removing the need for radical new tooling or completely different hydraulic steering systems to overcome the problems.
- Virtually the same components can be used as in the past with relatively small changes to the passageways in the lock valve and the function of the spool thereof.
- chatter is virtually eliminated by the invention since the valve spool is normally spaced-apart from any adjacent check balls.
- FIG. 1 is a schematic diagram of an hydraulic system according to an embodiment of the invention
- FIG. 2 is a front elevation of the combined steering pump and lock valve thereof
- FIG. 3 is a sectional view taken along line 3--3 of FIG. 2;
- FIG. 4 is a sectional view of a lock valve according to a second embodiment of the invention with the spool thereof partly broken away;
- FIG. 5 is sectional view of a lock valve according to a third embodiment of the invention.
- FIG. 1 shows an hydraulic steering system 10 of the type typically used on small pleasure craft and fishing boats. These systems include a rotary pump 11 which is rotated by means of a steering wheel 13.
- the particular pump 11 shown in FIG. 1 is of the two port type, having ports 15 and 17 which serve as intake ports and discharge ports for hydraulic fluid depending upon the direction the steering wheel 13 is turned. For example, if steering wheel 13 is rotated clockwise, port 17 acts as a discharge port and pumps hydraulic fluid. Port 15 acts as an intake port in this instance. The ports reverse their function when the wheel is rotated counter-clockwise.
- the ports 15 and 17 are connected to opposite sides of a double acting hydraulic cylinder 16 by hydraulic lines 12 and 14.
- the cylinder 16 in this example is coupled to an outboard motor 19 and causes the motor to rotate to steer the boat.
- lock valve 18 in the system which has a first port 21, a second port 22, a third port 23 and a fourth port 24.
- the function of lock valve 18 is similar to prior art lock valves. It stops a flow of fluid through hydraulic lines 12 and 14 except when port 21 or port 22 is pressurized according to the direction in which steering wheel 13 is rotated. If the steering wheel is released, then the lock valve prevents a flow of fluid through lines 12 and 14 and hence keeps cylinder 16 and motor 19 in the set position.
- the steering pump 11 and lock valve 18 are combined in a single pump unit 26 in the embodiment shown in FIG. 2 and 3.
- the unit is in a generally cylindrical housing 28.
- Lock valve 18 is located within housing 28 rearwardly of the pump 11 having a body 19. Ports 21 and 22 are connected to the pump, while ports 23 and 24 are connected to the cylinder 16 shown in FIG. 1. There is a cylindrical bore 30 within the housing which has a first end 32 and a second end 34. There is a chamber 36 for hydraulic fluid adjacent end 32 and a corresponding chamber 38 adjacent end 34.
- a first ball-type check valve 40 includes a ball 42 which is resiliently biased towards chamber 36 by a coil spring 48 pressing on a cup fitting 50 which engages the ball.
- the structure of the check valve is conventional and therefore is not described in more detail. Other types of one-way valves could be employed such as popper valves.
- check valve 54 adjacent chamber 38 having a ball 55.
- the structure is the same as check valve 40.
- passageway 56 extending from port 24 to the check valve 40.
- the check valve is opened when there is sufficient pressure in chamber 38 to allow fluid to flow from the chamber to port 24.
- the ball valve cannot be unseated by pressurized fluid at port 24 and therefore acts to prevent fluid from flowing from port 24 to chamber 38 and port 22 unless the check valve is opened by some other means.
- a spool valve 59 having a spool 60 reciprocatingly received within the bore 30.
- the spool has a first end 62 and a second end 64.
- the spool has a center portion 70 which is smaller in diameter than the end portions, therefore leaving an annular passageway 72 between this portion of the valve spool and the bore.
- protrusion 74 connected to end portion 66.
- the protrusion is coaxial with the bore 30 and the valve spool, as is check valve 40. It may be seen that protrusion 74 can contact the ball 42 to unseat the ball when the valve spool is moved towards ball 42 with sufficient force.
- the opposite end of the valve spool has a protrusion 80 which is similar to protrusion 74. Protrusion 80 can likewise unseat the ball 55 of ball valve 54 when pressed against the ball with sufficient force.
- passageway 82 which extends from port 21 to chamber 36.
- passageway 84 which extends from port 22 to chamber 38.
- valve 18 is generally similar in structure to some :prior art lock valves also adapted for use on marine hydraulic steering systems.
- valve 18 has an additional passageway 90 which extends from port 21 to bore 30 adjacent end portion 66 of the valve spool. When the valve spool is centered, passageway 90 is covered by end portion 66, thus blocking fluid from flowing from port 21 into bore 30.
- passageway 92 extending from port 22 to bore 30 adjacent end portion 68 of the valve spool. Again, when the valve spool is centered, that is at an equal distance between the ball valves, the passageway 92 is covered by end portion 66, thus preventing hydraulic fluid from flowing from port 22 into the bore.
- passageway 94 which extends from port 23 to bore 30 adjacent end portion 66 and generally opposite bore 90. Again, passageway 94 is covered by end portion 66 of the valve spool when centered.
- passageway 96 extending from port 24 to bore 30 adjacent end portion 68 of the valve spool generally opposite passageway 92. Again, passageway 96 is blocked by end portion 68 when the valve spool is centered, preventing hydraulic fluid from flowing to or from the bore 30 through the passageway.
- valve 18 and system 10 can be understood by referring to FIG. 1 and 3.
- the valve spool 60 When steering wheel 13 is released, and therefore no pressurized fluid is pumped towards ports 21 or 22 of the lock valve from the pump 11, the valve spool 60 is centered with an approximately equal gap between each of the protrusions 74 and 80 and the respective check valves. In this position of the valve spool, there can be no fluid flow through the lock valve.
- the passageways 90, 92, 94 and 96 communicating with the bore 30 are blocked by the end portions 66 and 68 of the valve spool.
- check valve 40 is seated, thus blocking the flow of fluid in either direction between chamber 36 and port 23 past the check valve.
- check valve 54 is seated, thus preventing a flow of fluid between chamber 38 and port 24 past the valve. Because no fluid can flow past the valve, the cylinder, 16 shown in FIG. 1 is held in position, thus ensuring that the motor 19 or rudder are kept in position on course without any force being applied to the steering wheel 13.
- a return flow of fluid from port 24 to port 22 does not depend upon the valve spool forcing open check valve 54. Instead, passageway 96 from port 24 can communicate with passageway 92 extending to port 22 when the valve spool 60 is moved towards chamber 38 by pressurized fluid in chamber 36. When this occurs, passageway 72 extending about the center portion 70 of the valve spool extends between passageways 92 and 96 as seen in FIG. 3.
- Ball valve 40 opens only after the return flow through passageways 92 and 96 is permitted. Then the fluid is free to pass through the lock valve in both directions.
- Valve 18.1 differs from valve 18 in one significant way; there are no protrusions on valve spool 60.1.
- Cheek valves 40.1 and 54.1 are unseated only for fluid flow from port 21.1 to port 23.1 and from port 22.1 to port 24.1 respectively.
- this embodiment has a vent passageway 100 in line with passageways 92.1 and 96.1.
- This vent passageway is connected to the reservoir and allows excess pressure to vent only when there is a return flow from passageway 96.1 to passageway 92.1.
- This vent passageway should preferably be on the side of the lock valve not normally receiving the prevailing lead.
- the vent may have an orifice of up to 0.04" diameter in this embodiment.
- FIG. 5 Another alternative embodiment is shown in FIG. 5 where like parts have like numbers as in FIG. 3 with the addition of "0.2".
- the right side of the valve from the point of view of the drawing, is essentially conventional.
- the left side in this embodiment completely does away with a ball valve.
- Valve spool 60.2 has a protrusion 74.2 on one end thereof only, that end being the first end which is adjacent check valve 40.2.
- port 21.2 When port 21.2 is pressurized, the spool is shifted to the left, from the point of view of FIG. 5, until passageway 72 is aligned with passageways 92.2 and 96.2.
- Valve 40.2 is then unseated by the pressure of fluid in chamber 36.2 which moves through passageways 82.2 and 52.2 to port 23.2.
- the return fluid enters port 24.2 and passes through passageway 96.2 to bore 30.2. The fluid therefore can pass through passageway 72.2 around center portion 70.2 of valve spool 60.2 and reach port 22.2 through passageway 92.2.
- pressurized fluid When pressurized fluid is pumped to port 22.2, it applies pressure to end 64.2 of the spool at chamber 38.2. This moves the spool to the right from the point of view of FIG. 2, until projection 74.2 of the spool contacts check valve 40.2.
- the pressurized fluid acts against end 64.2 of the spool, forcing open check valve 40.2 and permitting a return flow of fluid through port 23.2, passageway 52.2, chamber 36.2 and passageway 82.2 to port 21.2. Once this return flow path is established, passageways 96.2 and 92.2 thus are uncovered to the left of the spool, allowing discharge fluid to travel out port 24.2 to cylinder 18.
- this embodiment has a vent passageway 102 which communicates centrally on bore 30.2 via orifice 104. This allows excess pressure to slowly bleed to the reservoir (not shown). This orifice is 0.02" in diameter in this embodiment.
- the embodiment of FIG. 2 and 3 also has a vent passageway similar to this one or the passageway 100 of FIG. 4.
- FIG. 3 relies upon pressure equalization to center the spool after the helm is released.
- the spool can be centered by the use of springs, such as coil springs at each end of the valve spool.
Abstract
Description
Claims (12)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/104,642 US5349818A (en) | 1993-08-11 | 1993-08-11 | Low deadband marine hydraulic steering system |
CA002125516A CA2125516C (en) | 1993-08-11 | 1994-06-09 | Marine hydraulic steering system with reservoir returns |
US08/721,525 USRE36342E (en) | 1993-08-11 | 1996-09-26 | Low deadband marine hydraulic steering system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/104,642 US5349818A (en) | 1993-08-11 | 1993-08-11 | Low deadband marine hydraulic steering system |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US08/721,525 Reissue USRE36342E (en) | 1993-08-11 | 1996-09-26 | Low deadband marine hydraulic steering system |
Publications (1)
Publication Number | Publication Date |
---|---|
US5349818A true US5349818A (en) | 1994-09-27 |
Family
ID=22301564
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US08/104,642 Ceased US5349818A (en) | 1993-08-11 | 1993-08-11 | Low deadband marine hydraulic steering system |
US08/721,525 Expired - Lifetime USRE36342E (en) | 1993-08-11 | 1996-09-26 | Low deadband marine hydraulic steering system |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US08/721,525 Expired - Lifetime USRE36342E (en) | 1993-08-11 | 1996-09-26 | Low deadband marine hydraulic steering system |
Country Status (2)
Country | Link |
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US (2) | US5349818A (en) |
CA (1) | CA2125516C (en) |
Cited By (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5481871A (en) * | 1995-03-02 | 1996-01-09 | Teleflex (Canada) Ltd. | Hydraulic steering system with spool pressure equalization |
US5816359A (en) * | 1995-06-23 | 1998-10-06 | New Holland North America, Inc. | Control valve for a hydraulic steering system |
US6095187A (en) * | 1998-11-05 | 2000-08-01 | Interface Devices, Inc. | Solenoid-actuated zero-leakage fail-safe three-position poppet-style four-way hydraulic directional control valve |
US6361388B2 (en) | 1999-10-12 | 2002-03-26 | Glenn D. Foreman | Marine motor drive assembly |
US6524147B1 (en) | 2001-09-28 | 2003-02-25 | Mark X Steering Systems, Llc | Power assist marine steering system |
US6579072B2 (en) | 2001-07-27 | 2003-06-17 | Teleflex Canada Limited Partnership | Swash plate pump with low stress housing |
US6598553B1 (en) | 2002-02-13 | 2003-07-29 | Mark X Steering Systems, Llc | Power assist marine steering system |
EP1382845A2 (en) * | 2002-07-16 | 2004-01-21 | ULTRAFLEX S.p.A. | Oil pump for marine steering gear |
US20040237768A1 (en) * | 2003-05-28 | 2004-12-02 | Barber Dennis R. | Hydraulic control valve assembly having dual directional spool valves with pilot operated check valves |
US20050076950A1 (en) * | 2003-08-07 | 2005-04-14 | Juergen Berbuer | Safety shut-off device |
US7325507B1 (en) * | 2005-05-27 | 2008-02-05 | Mark X Steering Systems Llc | Tiller operated marine steering system |
US7681513B1 (en) * | 2005-05-27 | 2010-03-23 | Mark X Steering Systems Llc | Tiller operated marine steering system |
US20120152629A1 (en) * | 2010-12-15 | 2012-06-21 | Mather Daniel T | Hydraulic system having load lock valve |
US20150075640A1 (en) * | 2013-09-13 | 2015-03-19 | Norbert J. Kot | Pneumatic Valve Assembly and Method |
US9132902B2 (en) | 2013-03-12 | 2015-09-15 | Clinton J. Angelle | Marine drive system and method |
US10619551B2 (en) | 2017-06-09 | 2020-04-14 | Clinton J. Angelle | Boat hull cooling and marine-drive system |
US10947890B2 (en) | 2018-06-09 | 2021-03-16 | Clint Angelle | Boat hull cooling and marine-drive system with auxiliary raw water cooling reservoir |
US11143110B2 (en) * | 2015-10-19 | 2021-10-12 | General Electric Company | Aeroderivative jet engine accessory starter relocation to main shaft—directly connected to HPC shaft |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6364280B1 (en) | 2000-06-02 | 2002-04-02 | Damir Anton Fox | Adjustable slow shift control unit |
US7254945B1 (en) * | 2006-02-27 | 2007-08-14 | Kayaba Industry Co., Ltd. | Operate check valve and hydraulic driving unit |
US7997398B1 (en) | 2008-03-31 | 2011-08-16 | Brunswick Corporation | Hydraulically actuated marine transmission |
FR2933471B1 (en) * | 2008-07-03 | 2013-02-15 | Vianney Rabhi | BALANCED ELECTRO-HYDRAULIC VALVE FOR A VARIABLE COMPRESSION RATE MOTOR HYDRAULIC CONTROL UNIT |
US20100090143A1 (en) * | 2008-08-28 | 2010-04-15 | Kot Norbert J | Dual locking valve |
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US5018935A (en) * | 1989-11-09 | 1991-05-28 | Deere & Company | Automatic pressure relief system for a hydraulic motor |
US5036750A (en) * | 1989-08-29 | 1991-08-06 | Nippon Air Brake Kabushiki Kaisha | Pilot-operated dual check valve assembly with cross-line flow valving pilot pistons |
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-
1993
- 1993-08-11 US US08/104,642 patent/US5349818A/en not_active Ceased
-
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- 1994-06-09 CA CA002125516A patent/CA2125516C/en not_active Expired - Lifetime
-
1996
- 1996-09-26 US US08/721,525 patent/USRE36342E/en not_active Expired - Lifetime
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Cited By (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5481871A (en) * | 1995-03-02 | 1996-01-09 | Teleflex (Canada) Ltd. | Hydraulic steering system with spool pressure equalization |
US5816359A (en) * | 1995-06-23 | 1998-10-06 | New Holland North America, Inc. | Control valve for a hydraulic steering system |
US6095187A (en) * | 1998-11-05 | 2000-08-01 | Interface Devices, Inc. | Solenoid-actuated zero-leakage fail-safe three-position poppet-style four-way hydraulic directional control valve |
US6361388B2 (en) | 1999-10-12 | 2002-03-26 | Glenn D. Foreman | Marine motor drive assembly |
US6579072B2 (en) | 2001-07-27 | 2003-06-17 | Teleflex Canada Limited Partnership | Swash plate pump with low stress housing |
US6524147B1 (en) | 2001-09-28 | 2003-02-25 | Mark X Steering Systems, Llc | Power assist marine steering system |
US6598553B1 (en) | 2002-02-13 | 2003-07-29 | Mark X Steering Systems, Llc | Power assist marine steering system |
EP1382845A2 (en) * | 2002-07-16 | 2004-01-21 | ULTRAFLEX S.p.A. | Oil pump for marine steering gear |
US20040013540A1 (en) * | 2002-07-16 | 2004-01-22 | Giorgio Gai | Oil pressure operated pump for marine steering gears |
EP1382845A3 (en) * | 2002-07-16 | 2004-03-03 | ULTRAFLEX S.p.A. | Oil pump for marine steering gear |
US6984113B2 (en) | 2002-07-16 | 2006-01-10 | Ultraflex S.P.A. | Oil pressure operated pump for marine steering gears with a valve set shell with valves separately capable of assembly with the valve housing |
US20040237768A1 (en) * | 2003-05-28 | 2004-12-02 | Barber Dennis R. | Hydraulic control valve assembly having dual directional spool valves with pilot operated check valves |
US6871574B2 (en) | 2003-05-28 | 2005-03-29 | Husco International, Inc. | Hydraulic control valve assembly having dual directional spool valves with pilot operated check valves |
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US11143110B2 (en) * | 2015-10-19 | 2021-10-12 | General Electric Company | Aeroderivative jet engine accessory starter relocation to main shaft—directly connected to HPC shaft |
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Also Published As
Publication number | Publication date |
---|---|
CA2125516A1 (en) | 1995-02-12 |
CA2125516C (en) | 1999-10-26 |
USRE36342E (en) | 1999-10-19 |
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